EP0114642B1 - Machine à bobiner - Google Patents

Machine à bobiner Download PDF

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Publication number
EP0114642B1
EP0114642B1 EP84100433A EP84100433A EP0114642B1 EP 0114642 B1 EP0114642 B1 EP 0114642B1 EP 84100433 A EP84100433 A EP 84100433A EP 84100433 A EP84100433 A EP 84100433A EP 0114642 B1 EP0114642 B1 EP 0114642B1
Authority
EP
European Patent Office
Prior art keywords
rotation
rotors
fact
winding machine
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired
Application number
EP84100433A
Other languages
German (de)
English (en)
Other versions
EP0114642A1 (fr
Inventor
Heinz Dr. E.H. Schippers
Erich Dr.-Ing. Lenk
Herbert Turk
Herbert Schiminski
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Oerlikon Barmag AG
Original Assignee
Barmag Barmer Maschinenfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from DE19833307915 external-priority patent/DE3307915A1/de
Application filed by Barmag Barmer Maschinenfabrik AG filed Critical Barmag Barmer Maschinenfabrik AG
Publication of EP0114642A1 publication Critical patent/EP0114642A1/fr
Application granted granted Critical
Publication of EP0114642B1 publication Critical patent/EP0114642B1/fr
Expired legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H54/00—Winding, coiling, or depositing filamentary material
    • B65H54/02—Winding and traversing material on to reels, bobbins, tubes, or like package cores or formers
    • B65H54/28—Traversing devices; Package-shaping arrangements
    • B65H54/2836—Traversing devices; Package-shaping arrangements with a rotating guide for traversing the yarn
    • B65H54/2839—Traversing devices; Package-shaping arrangements with a rotating guide for traversing the yarn counter rotating guides, e.g. wings
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2701/00—Handled material; Storage means
    • B65H2701/30—Handled filamentary material
    • B65H2701/31—Textiles threads or artificial strands of filaments

Definitions

  • the invention relates to a winding machine for winding threads into cross-wound bobbins.
  • This winding machine is particularly suitable for continuously starting threads, in particular synthetic threads, which start up and wind up continuously at speeds of more than 6000 m / min.
  • the axial distance between the traversing stroke ranges is still very large.
  • This invention achieves the object of designing such a winding machine in such a way that it is suitable for winding up a plurality of threads and that a plurality of threads starting from the same direction or running in parallel can be wound up in a plurality of winding regions lying close to one another.
  • the adjacent stroke areas are very close to each other, that the bobbin tubes can be clamped on a bobbin spindle and lie close to one another or abut one another on the end face, and just about the space required on each bobbin tube to form a waste winding and a thread reserve winding remains.
  • the advantage of the known winding machine that all driver arms (hereinafter abbreviated to "wing") are distributed in only two planes of rotation is retained according to the invention. This ensures that there is the smallest possible distance between the wings and that the distance between the planes of rotation of the wings and the line of the thread on an upstream guide roller is as small as possible. This is a prerequisite for an exact depositing of the thread on the bobbin according to a filing law, which ensures a perfect winding structure with optimal running conditions of the thread from the bobbin.
  • the rotating circles of adjacent rotors can overlap in a maximally large area without hitting one another or hindering one another.
  • the aligned arrangement of the guide rollers ensures that the bobbins arranged behind them can be arranged as desired, provided only the drag length of the thread between the guide roller and the surface line of the bobbin, on which the thread runs onto the bobbin, from bobbin to bobbin at least approximately the same and is only short.
  • the bobbins can be arranged in alignment on a single bobbin spindle and can always be of the same thickness.
  • the coils can be in circumferential contact with the guide roller or have a small distance.
  • the coils can also be clamped in individual holders and can have different thicknesses. Furthermore, it can be conical cross-wound bobbins, which lie with a surface line on or parallel to the guide roller.
  • two, but also three and more stroke ranges can be arranged in alignment with one another.
  • a particularly favorable ratio of traversing stroke length and distance between the individual stroke areas is achieved if each of the rotors has three driver arms offset by 120 °, the driver arms of adjacent stroke areas which are arranged in identical rotary planes being offset in the overlap area with the same direction of movement and essentially symmetrically Comb phase.
  • the wings preferably have on their side facing away from the pushing edge a leading edge - referred to in this application as a "brake flag" - which is shaped in such a way that its point of intersection with the guide ruler moves essentially at the traversing speed in the direction of the traversing stroke center. This prevents the thread from moving faster to the center of the traversing stroke than corresponds to the guide speed of the pushing edge of the wing traveling to the center of the traversing stroke.
  • the guide ruler lies on the side of the thread running plane on which the gear of the rotors is located and also that the guide ruler can be moved away from the rotor axes until the driver arms no longer cover the guide ruler.
  • this embodiment offers the advantageous possibility of providing the guide ruler with a thread catching and thread guide notch outside of its traversing stroke. When the guide ruler moves out of the overlap area with the wings of the traversing device, the thread slides into this thread guide notch. This thread guide notch is advantageously arranged on both sides of the traverse stroke.
  • the ruler can serve as a thread guide in this version, z. B. to guide the running thread in a catch zone and / or a thread reserve zone of the bobbin case.
  • the guide rule be designed as a positive guidance at least in some areas.
  • the guide ruler has a front and a rear guide rail. This makes it possible to prevent the thread from lifting off the guide rail. This is particularly advantageous at the traversing stroke ends if the thread is to be laid there with increased accelerations and / or decelerations after a laying law.
  • the shape of the guideline also offers the advantageous possibility of realizing certain movement laws for the thread, in particular also the possibility of reducing the traversing speed of the thread in the central region of the traversing stroke, so that there is an accumulation of thread material which approx. 2% higher than the thread placement in the end areas.
  • the arrangement of the guideline on the side of the thread run, on which the gears of the rotors also lie, also gives the possibility of protecting the wings on the thread run and operating side by a protective strip, which extends in the thread running direction over the rotary planes of the wings extends beyond.
  • This protective strip is cantilevered at one end of the stroke area and extends parallel to a traverse stroke. At the other end of this stroke range, the shoulder strip forms a threading slot directed into the thread running plane. This design ensures that injuries from the rotating wing are avoided on the one hand, but on the other hand the wing is not in the thread operation, z. B. be damaged by the thread guide suction gun when threading.
  • the threading slot opens into a known thread reserve, which catches the thread, carries it over a few turns into the area of the traversing stroke and releases it there so that it can be caught by the wings.
  • the traversing device is preferably inclined in such a way that the rake planes of the wings enclose a smallest angle with the running plane of the threads in the region of the thread running towards the plane of rotation, which is between 45 ° and 70 °.
  • the guide roller From the guide roller, the thread is guided to the bobbin essentially free of drag lengths.
  • the guide roller can rest on the circumference of the spool. It is preferably provided that the guide roller is resiliently suspended so that it can avoid the roundness of the coil. Furthermore, this resilient suspension of the guide rollers enables the simultaneous use of drive rollers.
  • the resilient suspension of the guide rollers here prevents either the drive roller or the guide roller from lifting off the circumference of the spool in the course of the winding travel as the spool diameter increases.
  • the drive roller can simultaneously serve to increase the distance between the winding spindle axis and traversing with increasing winding diameter.
  • the drive roller and guide roller and traversing are mounted together on a slide, the guide roller being resiliently movable relative to this slide and the drive device of the slide being controlled as a function of the resilient deflection of the drive roller.
  • the traversing device is thus easy to maintain, especially when removing winders, that the gear and the drive of the rotors on the side facing the winding spindle the plane of rotation - i.e. in the direction of the thread - lies behind the plane of rotation of the wing. This avoids the need to dismantle the gearbox of the rotors if winders have formed on the rotors.
  • one of the rotors has a hollow shaft which is rotatably mounted.
  • a shaft on which the other rotor is seated is eccentrically mounted in this hollow shaft.
  • the hollow shaft and the shaft can be separated from each other, e.g. B. driven by belts or gears.
  • the two rotors are set very precisely in relation to one another in one stroke area, so that an exact thread transfer from one wing to the other is guaranteed at the stroke ends (exact phase position)
  • that the hollow shaft and the shaft are connected to one another by gears, in particular by means of a countershaft mounted within the hollow shaft, which gears connects the hollow shaft and the shaft to one another in such a way that both rotate at the same speed but in the opposite direction of rotation and with an exact phase position.
  • This configuration offers the advantageous possibility of providing a housing as a structural unit for each stroke range, in which the two rotors of this stroke range are mounted.
  • This housing can be installed and removed independently of the other lifting ranges for maintenance and repair.
  • the exact phase relationship of the rotors to each other can be set in the manufacturer's factory during final assembly.
  • only one of the shafts is driven from the outside, preferably the hollow shaft.
  • a belt drive, gear drive, worm gear drive or the like can again be used for the drive.
  • the gear of the rotors, the blades of which are located in the upper rotary plane, as viewed in the direction of the thread, is above these blades and the gear of the rotors, the blades of which rotate in the lower rotary plane, is below this rotary plane.
  • the housing is preferably divided so that the upper housing part can be removed from the lower housing part, e.g. B. can swing away. This is also advantageous for removing the winder and other maintenance.
  • An advantageous gear connection of the rotors of a plurality of stroke ranges has a common worm shaft for the rotors each assigned to a rotary plane, on which the worms assigned to the individual rotors are alternately left and right-handed from stroke to stroke.
  • the rotors of a rotating plane are each driven by a tangential belt, which alternately wraps around the pulleys of the rotors in the left and in the right direction and runs between the rotors in a zigzag shape.
  • the rotors of a rotary plane can be driven by bevel gears from a drive shaft common to them, which extends over all traversing stroke ranges.
  • bevel gears sit alternately from stroke to stroke on the left side of a rotor and at the next stroke on the right side of the corresponding rotor.
  • the rotors of the other rotary plane are each also driven by one of these drive options or from the first rotor via intermediate gears in such a way that the speed for the rotors assigned to a traverse stroke is the same, but the direction of rotation is opposite and the required phase position for exact Thread transfer is guaranteed at the lifting ends.
  • the winding machine shown in cross section in FIG. 2 by a traversing stroke has, as essential components, the winding spindle 1 and the traversing device 2.
  • winding spindle 1 By a motor, not shown, connected to the winding spindle 1, the winding spindle is also Direction of rotation 4 driven. Several sleeves 5 are clamped in alignment on the winding spindle. A cross-wound bobbin 6 is formed from each thread 3 starting from a vertical direction on each tube 5 during a winding time that is identical for all (winding travel).
  • a winding spindle can typically run three or four or six or eight threads parallel to one another and wound up to a corresponding number of bobbins 6.
  • Each traversing device consists of several circumferential wings 7 and 8, which are arranged in two planes of rotation I and II. In front of these wings is a guide ruler 9, along which the thread slides as it traverses. It should be mentioned that the guideline can also lie on the other side of the thread running plane (shown in broken lines).
  • the rotation planes I, II and the plane 111, in which the guide rule 9 is arranged, are inclined such that the rotation planes form an angle alpha between 45 and 70 ° with the thread feed direction indicated by arrow 10. This ensures that a guide roller 11 can be attached at a very short distance below the plane of rotation II.
  • the thread is guided onto the respective bobbin 6 in contact with this guide roller.
  • the guide roller 11 is in circumferential contact on the coil 6.
  • the guide roller 11 can also be a short distance from the surface of the coil and driven to rotate.
  • the vanes 7 of each traversing device which rotate in the plane of rotation I, are seated on the rotor 12.
  • the shaft 15 of the rotor 12 is driven in rotation by the worm wheel 17 and worm 18.
  • Whose hollow shaft 16 is, as can be seen from FIGS. 1 and 3, 4, eccentrically mounted to the shaft 15 of the rotor 12, with eccentricity e.
  • the hollow shaft 16 of the rotor II is driven by worm wheel 19 and worm 20.
  • the rotors of a stroke range are driven in opposite directions of rotation, at the same speed and in a specific phase position.
  • each rotor 12 and 13 has three blades 7 and 8, which are offset from one another by the same angular distance of 120 °.
  • Two interacting rotors 12, 13 with their wings 7 and 8 therefore form a stroke area H along the guide ruler 9.
  • the stroke area extends over a central angle of essentially 60 °.
  • the symmetrical phase position of the wing stars of adjacent traversing areas is particularly clearly visible.
  • the rotor and the shaft 15 rotate in the first traversing area H1 counterclockwise (arrow 27). I.e. the wings 7 of the rotor 15.1 convey the thread to the left.
  • Fig. 1 the moment of thread transfer from a wing 8 on a wing 7 is shown.
  • the pair of rotors of the adjacent traversing area H2 also has an opposite eccentricity such that the center distances of the rotors, the blades of which lie in the same rotational planes, change from traversing area to traversing area, and that in two adjacent traversing strokes the center distance of the rotors of a rotating plane, e.g. B. 1, is not the center distance of the associated rotors of the rotary plane 11. If the smaller center distance is denoted by «A, the larger center distance is A + 2e.
  • worm shafts 29 and 30 are driven in the same direction by motor 31 and toothed belt drive 32.
  • the worms 20 on worm shaft 30 drive the worm wheels 17 of the shaft 15 of the rotor 12 (rotary plane I).
  • the worms 18 on worm shaft 29 drive the worm wheels 19 of the hollow shaft 16 of the rotor 13 (rotating plane 11).
  • the screws 18, 20 of a traversing area each have the same direction. The direction of travel of the screws 18 or 20 is alternating left-hand or right-hand from one traversing area to the traversing area.
  • FIG. 7 in normal section and in FIG. 5 in top view is distinguished from the exemplary embodiment described above in that the gears of the rotors are mounted on different sides of the rotational planes I and II.
  • Essentially identical bearings for the shafts 15 and 16 are used for the two rotors 12 and 13.
  • Both shafts are driven by a worm wheel 17, 18.
  • the worm wheels are connected to one another by gears by means of belt drives 39, preferably toothed belts. They are driven by drive motor 40.
  • the two housings 34 and 35 are connected to one another in the motor axis by hinge 36. As a result, the housing 34 can be pivoted away from the housing 35. This facilitates the maintenance of the wings 7 and 8, in particular the cleaning of any winders.
  • the traversing device 2 is movable on the guide rod 41 in guide carriages 42 in such a way that the traversing device can move in the vertical direction as the diameter of the coils 6 increases.
  • suitable drive and control devices can be provided, by means of which the contact pressure with which the guide roller 11 bears against the coil 6 is applied to a predetermined amount corrected and the movement of the traversing device is controlled. Compare e.g. B. DE-PS 25 32 164, US-PS 4 106 710.
  • the center distance of the shafts 15, the rotors and driving arms 7 of which are arranged in the plane of rotation I is small from the swinging stroke H1 to the swinging stroke H2 and large from the swinging stroke H2 to the swinging stroke H3
  • the eccentricity of the shafts 15/16 changes from traversing stroke to traversing stroke.
  • FIG. 6 shows a special design of the guide ruler 9, which is used in particular if - as shown in FIGS. 5 and 7 - the guide ruler lies on the same side of the thread as the traversing.
  • the guide ruler is provided with thread catch notches 33 outside the traversing area.
  • the guideline can be moved away from the rotors. As a result, the thread is pushed away from the turning area of the wing, as shown in dashed lines. The thread then slides to one or the other side of the hoist area and falls into one of the thread catch notches 33 arranged on both sides of the stroke area. It is now possible to catch the thread there and z. B. suction to perform the coil change. However, it is also possible to place the thread in the thread catching notch at the beginning of the winding travel and to have the guide 9 carry out transverse movements to catch the thread on the tube and / or to form a thread reserve.
  • the stroke ranges H are very close together and the distance B is only as large as it is for the formation of a waste winding and a thread reserve winding next to each other single coil is needed.
  • the bobbins or bobbin tubes do not have to be spanned on a single bobbin spindle, as is shown in the exemplary embodiment.
  • the invention can also be used if a plurality of bobbins are rotatably mounted on a corresponding number of bobbin holders or other devices such that the bobbins are substantially flush during the winding process and are so close to one another that the traversing devices overlap.
  • FIGS. 8 and 9 shows a tangential belt drive for driving the rotors of both levels of rotation.
  • FIG. 8 reference may be made to the description of FIG. 4 with the one difference that here the worm wheels 17 and 19 of FIG. 4 are replaced by pulleys 43 and 44. Otherwise, this is also a Example, in which the gearbox is on only one side of the rotary planes, as z. B. is also the case in the embodiment of FIG. 10.
  • Fig. 9 shows a top view of the pulleys 44 and 43. It can also be seen from Fig. 9 that the center distance of the rotors and pulleys 43, 44 changes from one traverse stroke to another between a large value and a small value.
  • the pulleys 43 are driven by the tangential belt 45. Each of the pulleys is wrapped around the tangential belt at a certain angle.
  • the tangential belt 45 runs zigzag between the pulleys 43.
  • the tangential belt 45 is preferably a toothed belt which has teeth on both sides.
  • the pulleys 44 are driven by tangential belts 46.
  • a common deflection pulley is designated, which can be driven by the drive motor, not shown, directly or via a gear or belt drive.
  • the further deflection pulley 48 serves to deflect the tangential belt 45 after it has passed between the pulleys 43.
  • the further deflection pulley 49 serves to deflect the tangential belt 46.
  • the guide carriage 42 is movable on the guide rod 41 relative to the coils 6.
  • the traversing devices according to the invention are mounted on the guide carriage 42.
  • the carriage 42 carries the guide rollers 11, which are pivotably mounted in pivot arms 51 with pivot axes 52.
  • the swivel arms are powered by power, z. B. disc spring assembly 53, which are loaded under pressure. As a result, the guide rollers 11 resiliently abut the coil.
  • the relative position of the swivel arm 51 to the guide carriage 42 can be scanned, for. B. by a nozzle-baffle plate system 54, the output signal of the schematically illustrated drive device (cylinder-piston unit 55) of the guide carriage 42 is given.
  • the cylinder-piston unit 55 is pressurized by pressure source 56 via throttle 57.
  • the pressure which is established behind the throttle depends on the gap width at the nozzle 54.
  • the guide roller 11 can also serve as a drive roller or as a control roller. Should the guide roller as Serve control roller, so its speed is measured continuously and the measured value given to an axle drive motor for the winding devices so that the peripheral speed of the coil remains constant with increasing bobbin diameter.
  • FIG. 11 shows a detail of the traversing housing according to FIG. 10. It is shown in FIGS. 10 and 11 that each traversing stroke area is covered by a protective strip 75 on the front of the machine.
  • This protective strip 75 in particular also covers the rotary planes I and II in the direction of the thread. On the one hand, this means that you cannot reach into the rotating wings. On the other hand, it is also prevented that one gets into the turning area of the wings when threading with the thread suction gun and thereby damages the wings and their phase position.
  • the protective strip 75 forms a thread guide slot 76 with respect to the guide ruler 9 (not shown in FIG. 11).
  • Each protective strip 75 is cantilevered at one end, while at the other end it forms a threading opening 77 which opens into the guide groove 79 of a thread reserve device 78.
  • the thread reserve device 78 is slowly moved in the direction of the arrow 80 in the direction of the center of the traversing stroke. This creates a few turns of a thread reserve on the winding tube, which lies outside the normal traverse stroke range.
  • the thread reserve device 78 then moves out of the thread area in the direction of arrow 81. As a result, the released thread travels to the center of the traversing stroke and is caught by the wings of its respective traversing device.
  • Fig. 12 shows in the planes of rotation I and II the blades 7 and 8 with the rotors 12 and 13.
  • the rotors shown as shafts, are arranged on different sides of the planes of rotation.
  • Each rotor is driven by a bevel gear 58, 59.
  • the shafts 60, 61 which extend over several traversing areas and are driven in the synchronous direction by belt drive 62 by a drive motor, not shown, are used for the drive.
  • Further bevel gears 63, 64 are used to transmit the torque from the shafts 60, 61 to the bevel gears 58, 59. From one stroke area to the other, the bevel gears 63 alternately mesh with the bevel gears 58 of the respective rotors 12 on the left and right. The same applies to the engagement of the bevel gears 64 with the bevel gears 59 with respect to the rotors 13 or shaft 61.
  • the housing pot 65 which is round or oval or elliptical in plan view, the main axis lying in the direction of the eccentricity between the hollow shaft 16 and the shaft 15.
  • the shaft 15 of the vanes 8 is rotatably mounted in the housing pot 65.
  • the hollow shaft 16 of the vanes 7 is mounted in a housing cover 67 which also belongs to the structural unit. Cover 67 and housing pot 65 are firmly screwed together during assembly.
  • the hollow shaft has an internal gear rim 68, which has a tread 72 on the outside or toothing for a toothed wheel engagement or toothing for a toothed belt engagement.
  • the gear rim 68 is driven in the illustrated case by drive belts 73, for which purpose the housing pot 65 has a corresponding recess.
  • this unit can be preassembled in such a way that the phase position of the wings 7 and 8 is already set so that an exact thread transfer is guaranteed at the reversal points.
  • this assembly can be in the machine frame 74, i.e. H. the traversing housing. Then only the phase position of the rotors of adjacent traversing devices according to the invention has to be set by adjusting the gear engagement on the running surface 72.
  • FIGS. 14, 15 show exemplary embodiments which correspond to those in FIG. 10 over a wide range.
  • these embodiments have a drive roller 50.
  • This drive roller 50 is movably mounted in the guide carriage 42.
  • the bearing body 81 is guided in a straight guide in FIG. 15 and is supported against the guide carriage 42 by a plate spring assembly 82.
  • the nozzle 54 of a nozzle / baffle plate system is attached to the carriage 42. This nozzle 54 scans the movement of the bearing body 81 relative to the guide carriage 42.
  • the pressure in the support system (cylinder-piston unit 55) is influenced in such a way that, as the coil diameter increases, the distance between the nozzle and the baffle plate becomes smaller, and thus the pressure in the system increases, so that the guide carriage 42 moves upwards until the pressure balance is restored.
  • the guide rollers 11 and the drive rollers 50 are mounted on a common swivel frame 83.
  • the pivot frame is pivotable about pivot axis 84.
  • the pivot axis 84 is mounted in a bearing body 85 which is movable in a guide relative to the slide and is supported against the plate spring assembly 82.
  • the relative movement of the bearing body 85 is in turn sensed by a nozzle-baffle plate system 54 and the cylinder-piston unit 55 is given up.
  • FIGS. 16 and 17 show rotors which are suitable for producing coils with a Coil length of 100 mm and less, e.g. B. 85 mm. It turns out to be useful to accommodate the gears on the one hand to use rotors with four driver arms 7 and 8 in each plane of rotation I, II.
  • the driver arms 7 and 8 ⁇ are bent in such a way that only the ends of the driver arms 7 and 8 respectively in rotary level I or II rotate.
  • the rotors of the rotary planes I and II are at a short distance from one another in the drawing. However, this is only for illustration. In reality, all the driver arms 7 lie in only one level I and all the driver arms 8 in level II.
  • the driver arms are so long that their turning circle - at least with a small center distance of the adjacent rotor - covers its axis of rotation.
  • the arms can also be longer than the sum of stroke H and stroke distance B.
  • the driver arms 7 and 8 of a rotary plane - as is also described with reference to FIG. 1 - engage in a gearwheel-like manner.
  • the driver arms 7 penetrate the offset 86 of adjacent rotors.
  • gears of the rotors of the individual rotary planes I and II are divided.
  • the gear parts were on the side of the rotors facing away from the other rotating plane.
  • the gear structure corresponds to z. B. that of the embodiment of FIG. 7 or FIG. 12th
  • Relatively short projecting winding spindles can be used to accommodate several packages.

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  • Textile Engineering (AREA)
  • Winding Filamentary Materials (AREA)

Claims (32)

1. Machine à bobiner, pour bobiner plusieurs fils et former à chaque fois une bobine croisée, comportant des dispositifs de va-et-vient (2) par chacun desquels l'un des fils (3) subit, sur une plage d'excursion de va-et-vient (H) correspondant sensiblement à la longueur de bobine, un mouvement de pose selon un va-et-vient transversal à sa direction de défilement, contre une règle guide-fil, et ces dispositifs de va-et-vient consistent chacun en deux rotors (12, 13) entraînés dans des sens inverses et montés excentriquement l'un par rapport à l'autre (excentricité e), chacun d'eux ayant au moins deux bras d'entraînement (7, 8), les bras d'entraînement des deux rotors tournant dans deux plans de rotation (I, II) étroitement rapprochés, traversés par la trajectoire du fil, et les bras d'entraînement de plages d'excursion de va-et-vient voisines étant agencés dans les deux mêmes plans de rotation (I. Il), et les cercles de rotation de bras d'entraînement de plages d'excursion de va-et-vient voisines situés dans des plans de rotation différents (I et II) se recouvrant, caractérisé en ce que les rotors de deux plages (H) d'excursion de va-et-vient voisines dont les bras d'entraînement (7, 8) sont agencés dans des plans de rotation identiques (I ou II) sont entraînés dans des sens inverses et se recouvrent aussi, par leurs cercles de rotation, dans au moins l'un des plans de rotation, et en ce que les rotors dans ce plan de rotation (par exemple I) ont un petit entraxe, et les rotors dans l'autre plan de rotation (II) ont un entraxe important, augmenté de deux fois l'excentricité.
2. Machine à bobiner selon la revendication 1, caractérisée en ce que au moins trois plages d'excursion de va-et-vient sont prévues, et en ce que les rotors de plages voisines, dont les pales se trouvent dans un plan de rotation (par exemple I) ont, d'une plage d'excursion à l'autre, alternativement un petit entraxe et un grand entraxe agrandi de deux fois l'excentricité.
3. Machine à bobiner selon la revendication 1 ou 2, caractérisée en ce que chaque rotor (12, 13) possède trois bras d'entraînement (7, 8) mutuellement décalés de 120°, et en ce que les bras d'entraînement de plages d'excursion voisines qui sont agencés dans des plans identiques (I, II) engrènent mutuellement, de manière analogue à des dentures, et sensiblement symétriquement.
4. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que les bras d'entraînement ont un talon de freinage (21) écarté de leur direction de rotation, qui freine le mouvement de retour du fil vers le milieu d'excursion du va-et-vient, après l'inversion du mouvement d'excursion.
5. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que la règle guide-fil se trouve du même côté du défilement du fil que les mécanismes de transmission des rotors.
6. Machine à bobiner selon la revendication 5, caractérisée en ce que la règle guide-fil (9) est mobile dans une direction s'écartant des axes des rotors.
7. Machine à bobiner selon la revendication 6, caractérisée en ce que chaque règle guide-fil possède, à l'extérieur de sa plage d'excursion et au voisinage de celle-ci, une encoche (33) de retenue de fil.
8. Machine à bobiner selon la revendication 5, caractérisée en ce que de l'autre côté du défilement du fil, dans chaque plage d'excursion, il y a une barrette protectrice (75) qui, dans la direction de défilement du fil, recouvre les plans de rotation (I et II) et qui, à la première extrémité de la plage d'excursion, est fixée en porte-à-faux de façon telle qu'une fente d'enfilage (77) soit formée à l'autre extrémité de la plage d'excursion.
9. Machine à bobiner selon la revendication 8, caractérisée en ce que la fente d'enfilage (77) débouche dans un dispositif de réserve de fil (78).
10. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que les plans de rotation (I, II) des bras d'entraînement (7, 8) forment, avec le plan de défilement du fil arrivant, un angle de 45 à 70°.
11. Machine à bobiner selon la revendication 10, caractérisée en ce qu'un mécanisme de transmission des rotors se trouve du côté des plans de rotation (l, II) éloigné de la bobine.
12. Machine à bobiner selon la revendication 11, caractérisée en ce que les bobines sont entraînées par un cylindre d'entraînement tournant appliqué contre leur pourtour.
13. Machine à bobiner selon l'une des revendications 1 à 10, caractérisée en ce que le mécanisme de . transmission (22) des rotors (12, 13) se trouve du côté des plans de rotation tourné vers la bobine.
14. Machine à bobiner selon l'une des revendications 11 à 13, caractérisée en ce que le rotor (13) du plan de rotation (II) tourné vers le mécanisme de transmission est monté sur un arbre creux (16) dans lequel l'arbre (15) de l'autre rotor (12) du plan de rotation (I) est monté excentriquement.
15. Machine à bobiner selon la revendication 14, caractérisée en ce que l'arbre creux (16) est entraîné, de l'extérieur, par roue dentée ou courroie, et en ce que dans l'arbre creux est monté un arbre intermédiaire (66) par lequel la rotation de l'arbre creux est transmise, avec la même vitesse mais avec un sens de rotation inverse, à l'arbre (15).
16. Machine à bobiner selon la revendication 15, caractérisée en ce que l'arbre creux (16) ainsi que l'arbre (15) et l'arbre intermédiaire (66) sont montés dans un carter commun (65, 67) aménagé en tant qu'unité de montage, qui présente un ajour dans la région de la roue d'entraînement de l'arbre creux.
17. Machine à bobiner selon l'une des revendications 1 à 10 précédentes, caractérisée en ce que les mécanismes de transmission des rotors (12) dont les bras d'entraînement (7) se trouvent dans le plan de rotation supérieur (I) en considérant la direction de défilement du fil sont situés au-dessus de ce plan de rotation, et en ce que les mécanismes de transmission des rotors (13) dont les bras d'entraînement (8) se trouvent dans le plan de rotation inférieur (II) en considérant la direction de défilement du fil, sont situés en dessous de ce plan de rotation.
18. Machine à bobiner selon la revendication 17, caractérisée en ce que pour les mécanismes de transmission du groupe (12) de rotors de l'un des plans de rotation (I), et pour les mécanismes de transmission du groupe de rotors (13) de l'autre plan de rotation (II), il est prévu à chaque fois un carter séparé (34, 35), et en ce que les carters sont mobiles l'un par rapport à l'autre, le carter (34) des mécanismes de transmission du groupe de rotors (12) du plan de rotation supérieur - en considérant la direction de défilement du fil - étant par exemple relié par charnière (36) à l'autre carter (35), et pouvant être écarté de l'autre plan de rotation, par basculement.
19. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que les rotors (12, 13) d'un plan de rotation (par exemple 1) sont entraînés par un arbre à vis sans fin commun (29, 30), avec des vis (18, 20) dont les pas sont, d'une plage d'excursion à l'autre (H1, H2, H3, ...), alternativement à gauche et à droite.
20. Machine à bobiner selon l'une des revendications 1 à 18, caractérisée en ce que les rotors (12, 13) d'un plan de rotation (par exemple I) sont entraînés par un arbre d'entraînement commun (60), au moyen de roues coniques, les engrènements de roues coniques de rotors voisins étant alternativement tournés l'un vers l'autre et tournés dans des sens d'éloignement mutuel.
21. Machine à bobiner selon l'une des revendications 1 à 18, caractérisée en ce que les rotors d'un plan de rotation (par exemple I) sont entraînés par une courroie tangentielle (45), laquelle entoure partiellement les rotors des roues d'entraînement, alternativement vers la gauche et vers la droite, cela d'une plage d'excursion à l'autre, en formant un zigzag.
22. Machine à bobiner selon l'une des revendications 19, 20, 21 caractérisée en ce que les rotors des autres plans de rotation sont entraînés par les rotors du premier plan de rotation qui leur sont affectés, par des roues intermédiaires (68, 69, 70, 71), avec inversion du sens de rotation.
23. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que, au moins sur une zone partielle de leur plage d'excursion de va-et-vient, notamment dans les régions terminales de la plage de va-et-vient, les règles guide-fil (9) sont aménagées en tant que guidage forcé du fil avec un rail de guidage (37) devant le fil et un rail de guidage (38) derrière le fil.
24. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que, les cylindres de guidage (11) sont en contact périmétrique contre une ligne génératrice de la douille de canette (5) ou de la bobine croisée (6).
25. Machine à bobiner selon l'une quelconque des revendications précédentes, caractérisée en ce que la règle guide-fil est courbée de façon telle que, par rapport à la vitesse de va-et-vient moyenne, la vitesse de va-et-vient du fil soit accrue lors de l'entrée dans les plages d'inversion d'excursion et/ou lors de la sortie des plages d'inversion d'excursion.
26. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que la règle de guidage est courbée de façon que la vitesse de va-et-vient du fil au milieu de la plage d'excursion deva-et-vient soit de 1 à 4 % plus faible que la vitesse moyenne.
27. Machine à bobiner selon l'une des revendications précédentes, caractérisée en ce que le cylindre de guidage (11) est monté élastiquement (ressorts 53) par rapport à la bobine (6).
28. Machine à bobiner selon la revendication 27, caractérisée en ce que la déviation élastique du cylindre de guidage par rapport à la bobine est mesurée (gicleur 54), et en ce qu'un dispositif d'entraînement (55), par lequel l'entraxe du cylindre de guidage (11) et de la bobine est réglé en fonction du diamètre de bobine croissant, est commandé en fonction de la déviation du cylindre de guidage.
29. Machine à bobiner selon la revendication 12, caractérisée en ce que le dispositif de va-et-vient, les cylindres d'entraînement (50) et les cylindres de guidage (11) sont agencés sur un glissoir (42) mobile relativement aux bobines, et en ce que, sur ce glissoir, les cylindres d'entraînement sont montés fixes et rigides, tandis que les cylindres de guidage sont montés mobiles élastiquement.
30. Machine à bobiner selon la revendication 12, caractérisée en ce que les cylindres d'entraînement et les bobines sont montés, avec possibilité de mouvement relatif, de façon que l'entraxe puisse être accru, et en ce qu'en plus les cylindres d'entraînement, tout comme les cylindres de guidage, sont mobiles les uns par rapport aux autres et par rapport à la bobine, et en ce que le mouvement relatif des cylindres d'entraînement est mesuré et transmis à un dispositif d'entraînement (55), pour le réglage de l'entraxe.
31. Machine à bobiner selon la revendication 30, caractérisée en ce que les cylindres de guidage et les cylindres d'entraînement sont montés sur un dispositif porteur pivotant (83), qui est mobile par rapport à la bobine, et en ce que le mouvement relatif de ce dispositif porteur (83) est mesuré et transmis à la commande d'entraînement pour régler l'entraxe entre cylindres d'entraînement et cylindres de guidage, d'une part, et bobines d'autre part.
32. Machine à bobiner selon l'une des revendications 1 et 2, caractérisée en ce que les longueurs d'excursion sont inférieures à 110 mm, en ce que chaque rotor possède quatre bras d'entraînement mutuellement décalés de 90°, en ce que le rayon des bras d'entraînement est plus grand que le plus petit entraxe, notamment plus grand que la somme de la longueur d'excursion H et de l'intervalle B des plages d'excursion, en ce que les bras d'entraînement sont contrecoudés de façon telle que leurs extrémités tournent dans les plans de rotation respectifs (1, II), et en ce que les mécanismes de transmission des rotors, séparés selon les plans de rotation, sont agencés à chaque fois du côté du plan de rotation non tourné vers l'autre plan de rotation.
EP84100433A 1983-01-19 1984-01-17 Machine à bobiner Expired EP0114642B1 (fr)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE3301523 1983-01-19
DE3301523 1983-01-19
DE3302805 1983-01-28
DE3302805 1983-01-28
DE19833307915 DE3307915A1 (de) 1983-03-05 1983-03-05 Aufspulmaschine
DE3307915 1983-03-05
DE3310161 1983-03-21
DE3310161 1983-03-21

Publications (2)

Publication Number Publication Date
EP0114642A1 EP0114642A1 (fr) 1984-08-01
EP0114642B1 true EP0114642B1 (fr) 1986-05-28

Family

ID=27432905

Family Applications (1)

Application Number Title Priority Date Filing Date
EP84100433A Expired EP0114642B1 (fr) 1983-01-19 1984-01-17 Machine à bobiner

Country Status (3)

Country Link
US (1) US4505436A (fr)
EP (1) EP0114642B1 (fr)
DE (1) DE3460153D1 (fr)

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* Cited by examiner, † Cited by third party
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DE3417457A1 (de) * 1984-05-11 1985-11-14 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Aufspulmaschine
DE3843202A1 (de) * 1988-12-22 1990-10-04 Barmag Barmer Maschf Aufspulmaschine

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DE3513796A1 (de) * 1984-04-21 1985-12-05 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Aufspulvorrichtung
DE3560089D1 (en) * 1984-05-12 1987-04-23 Barmag Barmer Maschf Winding machine
EP0166292B1 (fr) * 1984-06-16 1987-09-16 B a r m a g AG Va et vient pour bobinoir
DE3664131D1 (en) * 1985-03-15 1989-08-03 Barmag Barmer Maschf Winding machine
EP0256383B1 (fr) * 1986-08-09 1990-01-31 B a r m a g AG Méthode pour embobiner des fils
DE3627879C2 (de) * 1986-08-16 1995-09-28 Barmag Barmer Maschf Verfahren zum Aufwickeln von Fäden
DE3831341C2 (de) * 1987-09-23 1994-09-01 Barmag Barmer Maschf Aufspulmaschine
DE3805347A1 (de) * 1988-02-20 1989-08-31 Barmag Barmer Maschf Aufspulmaschine
US4993650A (en) * 1988-11-07 1991-02-19 Appalachian Electronic Instruments, Inc. High speed precision yarn winding system
JP2560918B2 (ja) * 1990-12-28 1996-12-04 村田機械株式会社 トラバース装置
EP0768269B1 (fr) * 1992-08-19 1999-06-09 Toray Engineering Co., Ltd. Dispositif pour le bobinage de plusieurs fils
TW295102U (en) * 1992-12-23 1997-01-01 Barmag Barmer Maschf Cross winding machine
DE4304055C1 (de) * 1993-02-11 1994-03-24 Neumag Gmbh Changiervorrichtung
DE4317087A1 (de) * 1993-05-21 1994-11-24 Neumag Gmbh Vorrichtung zum Aufwickeln von Fäden
DE4425133C2 (de) * 1994-07-15 1997-03-13 Neumag Gmbh Aufspulmaschine
KR970006572A (ko) * 1995-07-01 1997-02-21 도바리 시게다까 방사 트래버스 장치
TW333208U (en) * 1996-03-14 1998-06-01 Murata Machinery Ltd Filament yarn traverse motion device
WO1998016457A1 (fr) * 1996-10-12 1998-04-23 Barmag Ag Machine de bobinage pour fil arrivant en continu
WO1998016458A1 (fr) * 1996-10-12 1998-04-23 Barmag Ag Bobineuse
EP0965554A3 (fr) * 1998-06-17 2000-08-16 Murata Kikai Kabushiki Kaisha Mécanisme de va-et-vient de fil et bobinoir muni d'un tel mécanisme
DE102011114025A1 (de) * 2011-09-21 2013-03-21 Oerlikon Textile Gmbh & Co. Kg Aufspulmaschine
DE102019000711A1 (de) 2019-01-31 2020-08-06 Oerlikon Textile Gmbh & Co. Kg Changiereinrichtung

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Publication number Priority date Publication date Assignee Title
DE3417457A1 (de) * 1984-05-11 1985-11-14 Barmag Barmer Maschinenfabrik Ag, 5630 Remscheid Aufspulmaschine
DE3843202A1 (de) * 1988-12-22 1990-10-04 Barmag Barmer Maschf Aufspulmaschine

Also Published As

Publication number Publication date
EP0114642A1 (fr) 1984-08-01
DE3460153D1 (en) 1986-07-03
US4505436A (en) 1985-03-19

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